CN104420496A - Shovel - Google Patents
Shovel Download PDFInfo
- Publication number
- CN104420496A CN104420496A CN201410400101.8A CN201410400101A CN104420496A CN 104420496 A CN104420496 A CN 104420496A CN 201410400101 A CN201410400101 A CN 201410400101A CN 104420496 A CN104420496 A CN 104420496A
- Authority
- CN
- China
- Prior art keywords
- mentioned
- pressure
- boost pressure
- engine
- supercharger
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2246—Control of prime movers, e.g. depending on the hydraulic load of work tools
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F3/00—Dredgers; Soil-shifting machines
- E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
- E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
- E02F3/36—Component parts
- E02F3/42—Drives for dippers, buckets, dipper-arms or bucket-arms
- E02F3/425—Drive systems for dipper-arms, backhoes or the like
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2282—Systems using center bypass type changeover valves
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2292—Systems with two or more pumps
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2296—Systems with a variable displacement pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B2037/122—Control of rotational speed of the pump
Landscapes
- Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Civil Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Operation Control Of Excavators (AREA)
- Supercharger (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
The invention provides a shovel which can maintain engine output even though boost pressure is difficult to increase as needed. The shovel includes an engine (11) with a variable exhaust nozzle turbine motor (25), and a controller (30) controlling rotating speed of the turbine shaft (25c) of the variable exhaust nozzle turbine motor (25). The controller increases the rotating speed of the turbine shaft (25c) before hydraulic pressure load is applied, so as to increase boost pressure of the variable exhaust nozzle turbine motor (25). The controller (30) increases the rotating speed of the turbine shaft (25c) before hydraulic pressure load is applied through reducing nozzle opening of a nozzle bucket (25a).
Description
Technical field
The present invention relates to a kind of excavator, the working oil that the hydraulic pump driven is spued is supplied to hydraulic actuator carries out operation by internal combustion engine.
Background technology
In recent years, as the engine of hydraulic excavator, use the situation of the engine of band turbocharger (turbo-supercharging machine) more (such as with reference to patent document 1).The pressure that turbocharger obtains utilizing the exhaust of engine to make turbine turn round imports to the suction system of engine, thus carries out supercharging to increase engine output.
Specifically, if start the driving of swing arm when excavator operates, then hydraulic pressure load increases, and also increases the engine load of the engine maintaining certain rotating speed before.For the increase of this engine load, engine, in order to maintain engine speed, increases engine by increase boost pressure (Boost pressure) and fuel injection amount and exports.
Especially, the output-controlling device disclosed in patent document 1, in order to promptly tackle the increase of engine load, is detecting that the operation time control that engine load increases is made as, and improves the boost pressure of the engine of band turbocharger, increases engine and exports.
Patent document 1: Japanese Unexamined Patent Publication 2008-128107 publication
But the output-controlling device disclosed in patent document 1 increases boost pressure when increase hydraulic pressure load being detected.That is, the hydraulic pressure load caused in external force such as excavating counter-force increases boost pressure after increasing a certain degree.Therefore, when causing hydraulic pressure load sharply to increase owing to excavating the external force such as counter-force for the output of engine, the increase of boost pressure cannot be made to follow the increase of this hydraulic pressure load, cause the deficiency that engine exports, there is the possibility stopping engine.
Summary of the invention
Therefore, even if desirable to provide a kind of when being difficult to increase boost pressure as required, the excavator that engine exports also can be maintained.
A kind of excavator of embodiments of the invention, possesses: lower running body; Upper rotation, is mounted on above-mentioned lower running body; Swing arm, is arranged in above-mentioned upper rotation; Swing arm cylinder, drives above-mentioned swing arm; Dipper, is arranged on above-mentioned swing arm; Dipper cylinder, drives above-mentioned dipper; Hydraulic pump, is mounted in above-mentioned upper rotation, and to above-mentioned swing arm cylinder and above-mentioned dipper cylinder supply working oil; Internal combustion engine, is mounted in above-mentioned upper rotation, possesses supercharger, and is controlled as certain rotating speed under the state be connected with above-mentioned hydraulic pump; And control device, control the rotating speed of above-mentioned supercharger, above-mentioned control device increased the rotating speed of above-mentioned supercharger to increase the boost pressure of above-mentioned supercharger before applying hydraulic pressure load.
Invention effect:
According to such scheme, even if the excavator that also can maintain engine output when being difficult to increase boost pressure as required can be provided.
Accompanying drawing explanation
Fig. 1 is the lateral view of the excavator of embodiments of the invention.
Fig. 2 is the block diagram of the structure example of the drive system of the excavator representing Fig. 1.
Fig. 3 is the skeleton diagram of the structure example representing the hydraulic system that the excavator of Fig. 1 carries.
Fig. 4 is the skeleton diagram of the structure example representing the supercharger that the excavator of Fig. 1 carries.
Fig. 5 represents that boost pressure increases the flow chart of the flow process of process.
Fig. 6 is the figure that various physical quantitys when representing the boost pressure increase process performing Fig. 5 are passed in time.
Fig. 7 represents that other boost pressures increase the flow chart of the flow process of process.
Fig. 8 represents that other boost pressures increase the flow chart of the flow process of process.
Fig. 9 is the figure that various physical quantitys when representing the boost pressure increase process performing Fig. 8 are passed in time.
Figure 10 is the skeleton diagram of other structure example representing supercharger.
Symbol description
1 lower running body
1A, 1B walking hydraulic motor
2 rotating mechanisms
2A rotation hydraulic motor
3 upper rotation
4 swing arms
5 dippers
6 scraper bowls
7 swing arm cylinders
8 dipper cylinders
9 scraper bowl cylinders
10 driver's cabins
11 engines
11a exhaust opening
13,13L, 13R adjuster
14,14L, 14R main pump
15 pioneer pumps
17 control valves
18L, 18R negative control choke valve
25 superchargers (variable nozzle turbine)
25a nozzle vane
25b turbo blade
25c turbine wheel shaft
25d compressor blade
26 operating means
26A swing arm action bars
29,29A pressure sensor
30 controllers
40L, 40R center bypass line
41L, 41R bear pressure control pipeline
50 switches
60 boost pressure adjustment parts (nozzle actuators)
60a supercharger electro-motor
75 engine speed adjustment knobs
170 ~ 178 flow control valves
300 boost pressures increase wants no detection unit
301 Pressure control portions
P1 atmosphere pressure sensor
P2 spues pressure sensor
Detailed description of the invention
First, the excavator of embodiments of the invention is described with reference to Fig. 1.In addition, Fig. 1 is the lateral view of the excavator of the present embodiment.On the lower running body 1 of the excavator shown in Fig. 1, be equipped with upper rotation 3 via rotating mechanism 2.Upper rotation 3 is provided with operation fixture.Operation fixture such as comprises swing arm 4, dipper 5 and scraper bowl 6.Specifically, upper rotation 3 is provided with swing arm 4, in the front end of swing arm 4, dipper 5 is installed, in the front end of dipper 5, scraper bowl 6 is installed.Swing arm 4, dipper 5 and scraper bowl 6 be passive arm cylinder 7, dipper cylinder 8 and scraper bowl cylinder 9 hydraulic-driven respectively.Upper rotation 3 is provided with driver's cabin 10, and is equipped with power source such as engine 11 grade.
Fig. 2 is the block diagram of the structure example representing the drive system that the excavator of Fig. 1 carries, and represents mechanical dynamic system, high-pressure and hydraulic pipeline, pilot line and electric control system respectively with doublet, solid line, dotted line and dotted line.
The drive system of excavator mainly comprises engine 11, adjuster 13, main pump 14, pioneer pump 15, control valve 17, operating means 26, pressure sensor 29, controller 30, atmosphere pressure sensor P1, the pressure sensor P2 that spues, supercharger 25 and engine speed adjustment knob 75.
Engine 11 is drive sources of excavator, such as, be the diesel motor of the internal combustion engine as the mode action to maintain predetermined rotating speed.In addition, the output shaft of engine 11 is connected with the power shaft of main pump 14 and pioneer pump 15.In the present embodiment, certain rotating speed is controlled as under the state that engine 11 is connected with the power shaft of main pump 14 at its output shaft.
Adjuster 13 is devices of the discharge-amount for controlling main pump 14, such as, regulate the swash plate tilt angle of main pump 14 according to spue pressure or the control signal etc. of carrying out self-controller 30 of main pump 14, thus control the discharge-amount of main pump 14.
Main pump 14 is the hydraulic pumps for supplying working oil to control valve 17 via high-pressure and hydraulic pipeline, such as, be ramp type variable capacity type hydraulic pump.
Pioneer pump 15 is for via the hydraulic pump of pilot line to various hydraulic-pressure control apparatus supply working oil, such as, be fixed capacity type hydraulic pump.
Control valve 17 is the hydraulic control devices of the hydraulic system controlled in excavator.Control valve 17 such as optionally supplies to one or more components in swing arm cylinder 7, dipper cylinder 8, scraper bowl cylinder 9, walking hydraulic motor 1A (left use), walking hydraulic motor 1B (right use) and rotation hydraulic motor 2A the working oil that main pump 14 spues.In addition, below swing arm cylinder 7, dipper cylinder 8, scraper bowl cylinder 9, walking hydraulic motor 1A (left use), walking hydraulic motor 1B (right use) and rotation hydraulic motor 2A are referred to as " hydraulic actuator ".
Supercharger 25 is the devices forcibly sending into air to engine 11, such as, utilize the emission gases from engine 11 to increase pressure of inspiration(Pi) (generation boost pressure).In addition, supercharger 25 also can utilize the revolution of the output shaft of engine 11 to produce boost pressure.In the present embodiment, supercharger 25 is the variable nozzle turbine that can carry out the flow of control discharge gas according to the rotating speed of engine 11.In addition, variable nozzle turbine 25 is described in detail later.
Operating means 26 is devices that operator uses to operate hydraulic actuator, supplies the working oil spued by pioneer pump 15 via pilot line to the pilot port of the flow control valve corresponding with each hydraulic actuator.In addition, the pressure (first pilot) of the working oil supplied to each pilot port corresponds to the bar of the operating means 26 corresponding with each hydraulic actuator or the direction of operating of pedal (not shown) and the pressure of operational ton.
Pressure sensor 29 is sensors of the content of operation for detecting the operator employing operating means 26, such as detect the bar of operating means 26 corresponding with each hydraulic actuator or the direction of operating of pedal and operational ton with the form of pressure, and to the value that controller 30 output detections arrives.In addition, the content of operation of operating means 26 also can use other sensors beyond pressure sensor to detect.
Controller 30 is the control device for controlling excavator, such as, be made up of the computer possessing CPU (CentralProcessing Unit), RAM (Random Access Memory), ROM (Read Only Memory) etc.In addition, controller 30 reads to increase with boost pressure from ROM and wants the corresponding respectively program of no detection unit 300 and Pressure control portion 301 and be loaded into RAM, makes the process of CPU execution difference correspondence.
Specifically, controller 30 receives the detected value that pressure sensor 29 grade exports, and according to these detected values, performs boost pressure and increases and want the respective process of no detection unit 300 and Pressure control portion 301.Afterwards, controller 30 suitably supercharger 25 grade is exported and boost pressure increases will control signal corresponding to the respective result of no detection unit 300 and Pressure control portion 301.
More particularly, boost pressure increases the boost pressure wanting no detection unit 300 to determine whether to need increase supercharger 25.Further, when boost pressure increase wants no detection unit 300 to be judged to need to increase boost pressure, Pressure control portion 301 drives boost pressure adjustment part 60 described later, the boost pressure of adjustment supercharger 25.
Atmosphere pressure sensor P1 is for detecting atmospheric sensor, and to the value that controller 30 output detections arrives.In addition, the pressure sensor P2 that spues is the sensor of the pressure that spues for detecting main pump 14, and to the value that controller 30 output detections arrives.
Engine speed adjustment knob 75 is the devices for switch engine rotating speed.In the present embodiment, engine speed adjustment knob 75 can with stage switch engine rotating speeds more than 3 stages.Rotating speed controls to be certain with the engine speed set by engine speed adjustment knob 75 by engine 11.
At this, the hydraulic system that the excavator with reference to Fig. 3 key diagram 1 carries.In addition, Fig. 3 is the skeleton diagram of the structure example representing the hydraulic system that the excavator of Fig. 1 carries, same with Fig. 2, represents mechanical dynamic system, high-pressure and hydraulic pipeline, pilot line and electric control system respectively with doublet, solid line, dotted line and dotted line.
In figure 3, hydraulic system makes working oil circulate to operating oil tank via center bypass line 40L, 40R respectively from main pump 14L, 14R of being driven by engine 11.In addition, main pump 14L, 14R corresponds to the main pump 14 of Fig. 2.
Center bypass line 40L is through the high-pressure and hydraulic pipeline of the flow control valve 171,173,175 and 177 be configured in control valve 17, and center bypass line 40R is through the high-pressure and hydraulic pipeline of the flow control valve 170,172,174,176 and 178 be configured in control valve 17.
Flow control valve 173,174 is that the working oil in order to main pump 14L, 14R be spued supplies to swing arm cylinder 7 and discharged and the guiding valve of the flowing of switch operating oil to operating oil tank by the working oil in swing arm cylinder 7.In addition, flow control valve 174 is the guiding valves worked all the time when swing arm action bars 26A operates.In addition, flow control valve 173 is the guiding valves only worked when operating more than swing arm action bars 26A is with scheduled operation amount.
Flow control valve 175,176 is that the working oil in order to main pump 14L, 14R be spued supplies to dipper cylinder 8 and discharged and the guiding valve of the flowing of switch operating oil to operating oil tank by the working oil in dipper cylinder 8.In addition, flow control valve 175 is the valves worked all the time when dipper action bars (not shown) operates.In addition, flow control valve 176 is the valves only worked when operating more than dipper action bars is with scheduled operation amount.
Flow control valve 177 is that the working oil in order to make main pump 14L spue circulates and the guiding valve of the flowing of switch operating oil in rotation hydraulic motor 2A.
Flow control valve 178 is that the working oil for being spued by main pump 14R supplies and the guiding valve of being discharged to operating oil tank by the working oil in scraper bowl cylinder 9 to scraper bowl cylinder 9.
Adjuster 13L, 13R regulate the swash plate tilt angle of main pump 14L, 14R according to the pressure that spues of main pump 14L, 14R, thus control the discharge-amount of main pump 14L, 14R.In addition, adjuster 13L, 13R corresponds to the adjuster 13 of Fig. 2.Specifically, adjuster 13L, 13R, when the pressure that spues of main pump 14L, 14R reaches more than predetermined value, regulate the swash plate tilt angle of main pump 14L, 14R, thus reduce discharge-amount.This is the shaft horsepower in order to prevent from exceeding with the absorbed horsepower of pressure with the main pump 14 of the product representation of discharge-amount that spue engine 11.In addition, this control is called " full power control ".
Swing arm action bars 26A is an example of operating means 26, uses to operate swing arm 4.In addition, the working oil that swing arm action bars 26A utilizes pioneer pump 15 to spue, makes the control pressure corresponding with bar operational ton import to the some pilot port in left and right of flow control valve 174.In addition, swing arm action bars 26A is when bar operational ton is more than scheduled operation amount, and any pilot port in the left and right to flow control valve 173 all imports working oil.
Pressure sensor 29A is an example of pressure sensor 29, detects operator to the content of operation of swing arm action bars 26A with the form of pressure, and to the value that controller 30 output detections arrives.Content of operation is such as bar direction of operating, bar operational ton (bar work angle) etc.
Left and right walking rod (or pedal), dipper action bars, scraper bowl action bars and rotation process bar (all not shown) are the operating means of rotation of walking for operating lower running body 1, the opening and closing of dipper 5, the opening and closing of scraper bowl 6 and upper rotation 3 respectively.These operating means are same with swing arm action bars 26A, the working oil utilizing pioneer pump 15 to spue, makes the control pressure corresponding with bar operational ton (or amount of pedal operation) import to the some pilot port in left and right of the flow control valve corresponding with each hydraulic actuator.In addition, operator is same with pressure sensor 29A to these operating means content of operation separately, and detected with the form of pressure by corresponding pressure sensor, detected value outputs to controller 30.
Controller 30 receives the output of pressure sensor 29A etc., exports control signal as required to adjuster 13L, 13R, changes the discharge-amount of main pump 14L, 14R.
Switch 50 is switches that switch controller 30 increases the work/stopping of the process (hereinafter referred to as " boost pressure increases process ") of the boost pressure of supercharger 25, such as, be arranged in driver's cabin 10.Operator, by switch 50 is switched to on-position, makes to perform boost pressure and increases process, by switch 50 is switched to open position, makes not perform boost pressure and increases process.Specifically, if switch 50 is switched to open position, then controller 30 forbids that boost pressure increases the execution wanting no detection unit 300 and Pressure control portion 301, and it is invalid their function to be set to.
At this, the negative control adopted in the hydraulic system of key diagram 3 controls.
Center bypass line 40L, 40R at each flow control valve 177 in most downstream, possess negative control choke valve 18L, 18R between 178 and operating oil tank.The flowing of the working oil that main pump 14L, 14R spue is born control choke valve 18L, 18R and is limited.Further, negative control choke valve 18L, 18R produce the control pressure (hereinafter referred to as " negative pressure control ") being used for controlled adjuster 13L, 13R.
Negative pressure control pipeline 41L, 41R represented by dashed line are the pilot line for the negative pressure control produced in the upstream of negative control choke valve 18L, 18R being delivered to adjuster 13L, 13R.
Adjuster 13L, 13R regulate the swash plate tilt angle of main pump 14L, 14R according to negative pressure control, thus control the discharge-amount of main pump 14L, 14R.In addition, the negative pressure control imported is larger, and adjuster 13L, 13R more reduce the discharge-amount of main pump 14L, 14R, and the negative pressure control imported is less, more increase the discharge-amount of main pump 14L, 14R.
Specifically, as shown in Figure 3, when any hydraulic actuator of excavator is not all operated (hereinafter referred to as " standby mode "), the working oil that main pump 14L, 14R spue arrives negative control choke valve 18L, 18R by center bypass line 40L, 40R.Further, the flowing of working oil that main pump 14L, 14R spues makes the negative pressure control produced in the upstream of negative control choke valve 18L, 18R increase.Its result, the discharge-amount of main pump 14L, 14R is reduced to and allows minimum discharge-amount by adjuster 13L, 13R, suppresses the working oil spued by the pressure loss (pumping pressure loss) when center bypass line 40L, 40R.
On the other hand, when certain hydraulic actuator is operated, the working oil that main pump 14L, 14R spue, via the flow control valve corresponding with the hydraulic actuator of operand, flows into the hydraulic actuator of operand.Further, the amount that the flowing of the working oil that main pump 14L, 14R spue makes arrival bear control choke valve 18L, 18R reduces or disappears, the negative pressure control that the upstream being reduced in negative control choke valve 18L, 18R produces.Its result, adjuster 13L, 13R of accepting the negative pressure control declined make the discharge-amount of main pump 14L, 14R increase, and make enough working oils be recycled to the hydraulic actuator of operand, drive the hydraulic actuator of operand effectively.
By said structure, the hydraulic system of Fig. 3 in stand-by mode, can suppress the energy dissipation in main pump 14L, 14R.In addition, energy dissipation comprises the pumping pressure loss that working oil that main pump 14L, 14R spue produces on center bypass line 40L, 40R.
In addition, the hydraulic system of Fig. 3 supplies the working oil of necessity and sufficiency effectively to the hydraulic actuator of target from main pump 14L, 14R when enabling hydraulic actuator work.
Then, with reference to Fig. 4, the function as the variable nozzle turbine 25 of supercharger is described.In addition, Fig. 4 is the skeleton diagram of the structure example representing variable nozzle turbine 25.
Variable nozzle turbine 25 mainly comprises nozzle vane 25a, turbo blade 25b, turbine wheel shaft 25c and compressor blade 25d.
Nozzle vane 25a is the component of the flow controlling the emission gases flowed from the exhaust opening 11a of engine 11 to turbo blade 25b.In the present embodiment, nozzle vane 25a is controlled by the nozzle actuators 60 as boost pressure adjustment part, to increase and decrease nozzle aperture (aperture area).
Turbo blade 25b accepts the emission gases of engine 11 and pivotal component, is combined with compressor blade 25d via turbine wheel shaft 25c.Therefore, the revolution of turbo blade 25b is delivered to compressor blade 25d via the revolution of turbine wheel shaft 25c.
Compressor blade 25d is the outer gas of compression and to the component that the air entry of engine 11 supplies, turns round and make outer gas forcibly flow into the air entry of engine 11 together with turbo blade 25b.
Nozzle actuators 60 is 1 examples of boost pressure adjustment part, drives multiple nozzle vane 25a to control multiple nozzle vane 25a nozzle aperture separately simultaneously simultaneously.
Specifically, nozzle actuators 60 is higher with the rotating speed of engine 11, makes the larger mode of nozzle aperture drive nozzle vane 25a.Upper figure in Fig. 4 represents the variable nozzle turbine 25 being in the state that engine speed is higher, nozzle opening ratio is larger.In this case, maintain the low state of the situation smaller than nozzle aperture by the pressure at expulsion of the emission gases of nozzle vane 25a, also maintain lower state by the relative velocity of the emission gases of turbo blade 25b.In addition, referred to by the relative velocity of the emission gases of turbo blade 25b, the difference of the flow velocity of the flow velocity by the emission gases of the exhaust opening 11a of engine 11 and the emission gases by turbo blade 25b.
On the other hand, the figure below in Fig. 4 represents the variable nozzle turbine 25 being in the state that engine speed is lower, nozzle aperture is smaller.In this case, maintain the high state of the situation larger than nozzle aperture by the pressure at expulsion of the emission gases of nozzle vane 25a, also maintain higher state by the relative velocity of the emission gases of turbo blade 25b.Its result, even if identical by the flow velocity of the emission gases of the exhaust opening 11a of engine 11, nozzle aperture is less, larger by the relative velocity of the emission gases of turbo blade 25b, and the rotating speed of turbo blade 25b also increases.Further, the rotating speed of the compressor blade 25d be combined with turbo blade 25b via turbine wheel shaft 25c also increases.Its result, compressor blade 25d makes boost pressure increase, and more air is supplied to the air entry of engine 11.
In addition, in the upper figure in Fig. 4, the stream between representing due to nozzle vane 25a with the arrow of fine line is wider, therefore by state that the relative velocity of the emission gases of turbo blade 25b is smaller.In addition, represent with the arrow of fine line the state that the revolution of turbine wheel shaft 25c is slow respectively in the upper figure in Fig. 4 and by the smaller state of the flow velocity of the air of compressor blade 25d.On the other hand, in the figure below in Fig. 4, the stream between representing due to nozzle vane 25a with the arrow of heavy line is narrow, therefore by state that the relative velocity of the emission gases of turbo blade 25b is larger.In addition, the revolution representing turbine wheel shaft 25c respectively with the arrow of heavy line in the figure below in Fig. 4 is than state faster and by the larger state of the velocity ratio of the air of compressor blade 25d.In addition, below the control of the nozzle aperture corresponding with engine speed of being undertaken by nozzle actuators 60 as above is called " usually controlling ".Usually controlled by this, controller 30, when engine speed is low, can improve charging efficiency, when this external engine speed is high, can reduce pressure at expulsion.
Also speed probe can be possessed as engine speed detecting unit.Controller also can carry out engine speed to maintain according to the engine speed detected the certain rotating speed control of what is called of predetermined value.Also the control loop that speed (rotating speed) FEEDBACK CONTROL is such can be constructed.According to this structure, even if the deviation that engine speed declines and produces between targeting engine rotating speed and the engine speed detected, fuel injection amount also can be increased to maintain engine speed.Also can replace engine speed and use the rotating speed (speed) of the motor generator set be connected with engine.
In addition, nozzle actuators 60 is except usually controlling, when boost pressure increase wants no detection unit 300 to be judged to need to increase boost pressure, according to the control signal that controller 30 exports, nozzle aperture A is adjusted to nozzle aperture As when the boost pressure less than nozzle aperture when usually controlling increases.In addition, below the control of this nozzle aperture of being undertaken by nozzle actuators 60 is called " boost pressure increases control ".
More particularly, boost pressure increase wants the excavator of no detection unit 300 such as on highland to be in standby mode, be judged to need to increase boost pressure.Further, 301 pairs, Pressure control portion nozzle actuators 60 exports control signal, makes the nozzle aperture A of nozzle vane 25a be adjusted to nozzle aperture As when boost pressure increases.
Then, illustrate that the controller 30 of the excavator of the present embodiment increases the process (hereinafter referred to as " boost pressure increases process ") of boost pressure as required with reference to Fig. 5.In addition, Fig. 5 represents that boost pressure increases the flow chart of the flow process of process, and controller 30 repeatedly performs this boost pressure with predetermined period and increases process.In addition, in the present embodiment, excavator is in the environment that the air such as highland force down, and switch 50 is manually switched to on-position, and therefore controller 30 can make boost pressure increase want no detection unit 300 and Pressure control portion 301 effectively to play a role.
First, the boost pressure of controller 30 increases and will judge whether excavator is in standby mode (step S1) by no detection unit 300.In the present embodiment, whether boost pressure increases will no detection unit 300 be that more than pre-level pressure judges whether excavator is in standby mode according to the pressure that spues of main pump 14.Such as, if the pressure that spues of main pump 14 is less than pre-level pressure, then boost pressure increases and will be judged to be that excavator is in standby mode by no detection unit 300.In addition, boost pressure increases and also will can judge whether excavator is in standby mode according to the pressure of hydraulic actuator by no detection unit 300.
When boost pressure increase want no detection unit 300 to be judged to be that excavator is in standby mode (there is not hydraulic pressure load) (step S1 is), controller 30 stops the usual control (step S2) of nozzle aperture.Further, the boost pressure of controller 30 starting nozzle aperture increases control, the nozzle aperture A of nozzle vane 25a is adjusted to nozzle aperture As (step S3) when the boost pressure less than nozzle aperture when usually controlling increases.In the present embodiment, 301 pairs, the Pressure control portion nozzle actuators 60 of controller 30 exports control signal.The nozzle actuators 60 receiving this control signal interrupts the usual control of nozzle aperture.Further, the nozzle aperture of nozzle vane 25a is reduced to nozzle aperture As when boost pressure increases.Thereby, it is possible to increase through the relative velocity of the emission gases of turbo blade 25b, improve the rotating speed of turbine wheel shaft 25c, increase through the flow velocity of the air of compressor blade 25d to increase boost pressure.
On the other hand, boost pressure increases when wanting no detection unit 300 to be judged to be that excavator is not in standby mode (hydraulic pressure load) (step S1's is no), controller 30 stops the boost pressure of nozzle aperture to increase control, the usual control (step S4) of starting nozzle aperture.Further, controller 30 changes the nozzle aperture A of nozzle vane 25a according to engine speed.
Like this, controller 30 increases boost pressure when standby mode.Therefore, boost pressure can be increased predetermined amplitude in advance by controller 30 before cause hydraulic pressure load increase because of external force.Its result, even if when cannot increase rapidly boost pressure because air forces down, also can decline (workability decline) causing engine speed or before engine stopping, producing the boost pressure corresponding to the hydraulic pressure load increased.
Then, with reference to Fig. 6, the various physical quantitys passing in time when performing boost pressure increase process is described.In addition, Fig. 6 is the figure of the passage of time representing these various physical quantitys, represents atmospheric pressure, bar operational ton, hydraulic pressure load (absorbed horsepower), nozzle aperture, boost pressure, fuel injection amount and engine speed passage of time separately successively from upper.In addition, passing represented by dashed line in Fig. 6 does not perform the passing during boost pressure increase process when representing that excavator is positioned at lowly (environment that atmospheric pressure is higher), represent that excavator does not perform passing when boost pressure increase processes when being positioned at highland (environment that atmospheric pressure is lower) in Fig. 6 with the passing that single dotted broken line represents.In addition, passing indicated by the solid line in Fig. 6 represents that excavator performs passing when boost pressure increase processes when being positioned at highland (environment that atmospheric pressure is lower).The passing represented with these 3 kinds of lines is for illustrating that in the mode of easy understand boost pressure increases the effect of process.Specifically, excavator is under the environment that the atmospheric pressure such as highland are lower, when not performing boost pressure and increasing process, even if will boost pressure be increased at the time point detecting hydraulic pressure load increase, also boost pressure cannot be increased as situation about being in the higher environment of atmospheric pressure, cause the deficiency that engine exports, there is the possibility that engine is stopped.And when performing boost pressure increase process under the environment that the atmospheric pressure such as highland are lower, excavator can prevent the deficiency that engine exports.
In the present embodiment, suppose such as to have carried out situation about operating for the bar of mobile dipper 5 to carry out excavating at moment t1.
First, in order to compare, not perform boost pressure when illustrating that excavator is in lowly (environment that atmospheric pressure is higher) and increasing the passage of time not performing various physical quantitys when boost pressure increase processes when processing and when excavator is in highland (environment that atmospheric pressure is lower).
At moment t1, in order to carry out excavation action, start the operation of dipper action bars.The operational ton (making the angle that action bars tilts) of dipper action bars increases from moment t1 to moment t2, and at moment t2, the operational ton of dipper action bars remains certain.That is, from moment t1, dipper action bars is tilted by operating, and at moment t2, the slope of dipper action bars keeps certain.
From the moment t2 that dipper action bars becomes the state tilted the most, due to the load applied dipper 5, spuing of main pump 14 presses liter, and the hydraulic pressure load of main pump 14 starts to rise.That is, the hydraulic pressure load of main pump 14 is as shown in dotted line and single dotted broken line, rises near moment t2.In addition, the hydraulic pressure load of main pump 14 is equivalent to the load of engine 11, and the load of engine 11 also rises together with the hydraulic pressure load of main pump 14.Its result, when excavator is in low (environment that atmospheric pressure is higher), the rotating speed of engine 11 is shown in dotted line maintains desired speed like that, but when excavator is in highland (environment that atmospheric pressure is lower), the rotating speed of engine 11 starts soon to decline to a great extent as shown in single dotted broken line after t2.This is because under the environment that atmospheric pressure is lower, boost pressure reduces, and cannot realize the engine corresponding to the load of engine 11 and export.
Specifically, if the load of engine 11 increases, then under normal conditions, the control of engine 11 is worked, and fuel injection amount increases.Thus, boost pressure also increases, and the efficiency of combustion of engine 11 improves, and the output of engine 11 also increases.But during low pressure, the increase of fuel injection amount is limited, the efficiency of combustion of engine 11 fully cannot be improved.Its result, cannot realize the engine corresponding to the load of engine 11 and export, and causes the rotating speed of engine 11 to reduce.
Therefore, controller 30, when excavator is in highland (environment that atmospheric pressure is lower), increases process by performing boost pressure, before carrying out bar operation, improving boost pressure.
In addition, at this, perform the various physical quantitys passing in time during boost pressure increase process when being in highland (environment that atmospheric pressure is lower) about excavator, same reference Fig. 6 is described.In figure 6, represent that excavator performs the various physical quantitys passing in time when boost pressure increase processes when being in highland (environment that atmospheric pressure is lower) with solid line.In addition, in figure 6, excavator is in no load condition to moment t1, and is in standby mode.
As the bar operation that operator carries out, as mentioned above, at moment t1, in order to carry out excavation action, start the operation of dipper action bars.The operational ton (making the angle that action bars tilts) of dipper action bars increases from moment t1 to moment t2, and at moment t2, the operational ton of dipper action bars remains certain.That is, from moment t1, dipper action bars is tilted by operating, and at moment t2, the slope of dipper action bars keeps certain.If start the operation of dipper action bars at moment t1, then dipper 5 starts mobile, if reach moment t2, then dipper action bars becomes the state tilted most.
When performing boost pressure and increasing process, the nozzle aperture A of nozzle vane 25a, before moment t1, before namely carrying out bar operation, is adjusted to nozzle aperture As when the boost pressure less than nozzle aperture when usually controlling increases by controller 30.Therefore, boost pressure is in the same higher state of the situation that is positioned at lowly (environment that atmospheric pressure is higher) with excavator.In addition, the state that the moment t2 that can become at dipper action bars the state tilted most rises immediately is in.In addition, if the hydraulic pressure load of controller 30 main pump 14 rises at moment t2, be then judged to be that excavator is not in standby mode, stop the boost pressure of nozzle aperture to increase and control, start and usually control.Its result, nozzle aperture is controlled as the value corresponding with engine speed.In addition, in figure 6, for the ease of understanding, nozzle aperture when usually controlling is represented as passes with certain value, but in fact it is according to changes such as engine speeds.
Nozzle aperture As when increasing by like this nozzle aperture A of nozzle vane 25a being adjusted to the boost pressure less than nozzle aperture when usually controlling, the moment t2 that can start to rise at hydraulic pressure load makes boost pressure increase immediately.
If after the time t2, then hydraulic pressure load rises, thus the load of engine 11 also increases, and send the instruction increasing fuel injection amount further, Fuel Consumption increases gradually.The recruitment of Fuel Consumption is now only the amount corresponding with the increase of hydraulic pressure load.This is because engine speed maintains desired speed, do not need the Fuel Consumption making engine speed increase.In addition, at moment t3, boost pressure rises to more than predetermined value, even if therefore hydraulic pressure load increases, engine 11 is also in the state that effectively can increase engine and export.
As mentioned above, before carrying out bar operation, the nozzle aperture A of nozzle vane 25a is adjusted to nozzle aperture As when increasing than boost pressure little when usually controlling, boost pressure can be increased before hydraulic pressure load starts the time point risen thus.
In addition, as mentioned above, under the environment that atmospheric pressure is higher, even if do not perform boost pressure to increase process, boost pressure (with reference to dotted line) has also been in higher state at moment t1.
Therefore, even if do not perform boost pressure to increase process, variable nozzle turbine 25 is also in the state that can increase rapidly boost pressure.In addition, engine 11 is in and engine speed decline (workability decline) or engine can not be caused to stop and can supplying the state of the driving force corresponding to the hydraulic pressure load that external force causes.
But under the environment that atmospheric pressure is lower, when not performing boost pressure and increasing process, boost pressure (with reference to single dotted broken line) is also in lower state at moment t2.In addition, owing to being in the lower environment of atmospheric pressure, therefore variable nozzle turbine 25 cannot increase boost pressure rapidly.Specifically, variable nozzle turbine 25 cannot realize enough boost pressures to moment t3, and engine 11 fully cannot increase fuel injection amount.
Its result, engine 11 cannot export the driving force making engine speed remain certain, but reduces engine speed (with reference to single dotted broken line), according to circumstances, cannot increase engine speed and directly stop.
Therefore, controller 30, under the environment that atmospheric pressure is lower, increases process, before moment t1 by performing boost pressure, namely, before carrying out bar operation, the nozzle aperture of nozzle vane 25a is adjusted to nozzle aperture As when increasing than boost pressure little when usually controlling.Therefore, boost pressure (with reference to solid line) has been in higher state at moment t2.
Its result, even if under the environment that atmospheric pressure is lower, the situation of the environment that variable nozzle turbine 25 is also higher with atmospheric pressure is same is in the state that can increase rapidly boost pressure.In addition, engine 11 is in and engine speed decline (workability decline) or engine can not be caused to stop and can supplying the state of the driving force corresponding to the hydraulic pressure load caused because of external force.
In this case, if at moment t2, dipper 5 touches ground, then with excavate counter-force increase correspondingly, hydraulic pressure load increase.Further, correspond to the increase of this hydraulic pressure load suitable with the absorbed horsepower of main pump 14, the load of engine 11 also increases.Now, engine 11, in order to maintain predetermined engine speed, can increase boost pressure rapidly by variable nozzle turbine 25.
Like this, controller 30, when atmospheric pressure is lower, reduced nozzle aperture before carrying out bar operation, boost pressure can be maintained higher level thus, after carrying out bar operation, lingeringly not increase boost pressure.Its result, can prevent the engine speed when having carried out bar operation from declining or engine stops.
Then, illustrate that boost pressure increases other embodiments of process with reference to Fig. 7.In addition, Fig. 7 represents that the boost pressure of the present embodiment increases the flow chart of the flow process of process.The boost pressure of Fig. 7 increases in process, and the decision condition in step S11 is different from the decision condition that the boost pressure of Fig. 5 increases the step S1 in processing, but step S2 ~ S4 that the boost pressure of step S12 ~ S14 and Fig. 5 increases process is identical.Therefore, describe step S11 in detail, omit the explanation of other steps.In addition, in the present embodiment, eliminate switch 50, controller 30 can make boost pressure increase want no detection unit 300 and Pressure control portion 301 effectively to play a role all the time.
In step s 11, boost pressure increases and wants no detection unit 300 to determine whether to meet excavator to be in standby mode and the atmospheric pressure of excavator periphery is less than the condition of pre-level pressure.In addition, in the present embodiment, controller 30, according to the output of the atmosphere pressure sensor P1 that excavator carries, judges whether the atmospheric pressure of excavator periphery is less than pre-level pressure.
Further, when being judged to meet above-mentioned condition (step S11 is), controller 30 performs step S12 and S13.
And when being judged to not meet above-mentioned condition (step S11's is no), controller 30 performs step S14.
Thus, controller 30 can realize increasing with the boost pressure of Fig. 5 the identical effect of situation about processing.
In addition, in the present embodiment of output using atmosphere pressure sensor P1, controller 30 can also decide the size of nozzle aperture As when boost pressure increases according to atmospheric size.Specifically, atmospheric pressure is lower, and controller 30 more reduces nozzle aperture As when boost pressure increases.In this case, controller 30 is according to atmospheric size, and when both boost pressure can be increased, the size of nozzle aperture As sets stage by stage, also can set with no stage.By this structure, the size of the nozzle aperture after the reduction in standby mode can control by controller 30 stage by stage or with no stage, can suppress energy dissipation further.
Then, illustrate that boost pressure increases other embodiments of process with reference to Fig. 8.In addition, Fig. 8 represents that the boost pressure of the present embodiment increases the flow chart of the flow process of process.The boost pressure increase process of Fig. 8 and atmospheric size independently, operate the time point started at bar, the temporary transient nozzle aperture reducing nozzle vane 25a.Therefore, in the present embodiment, eliminate switch 50, controller 30 can make boost pressure increase want no detection unit 300 and Pressure control portion 301 effectively to play a role all the time.But, also can use switch 50 or atmosphere pressure sensor P1, as long as the situation that atmospheric pressure is lower, just make the boost pressure of the present embodiment increase process and play a role.
First, the boost pressure of controller 30 increases and will judge whether excavator is in standby mode (step S21) by no detection unit 300.In the present embodiment, with the boost pressure of Fig. 5 increase process same, boost pressure increase want no detection unit 300 according to main pump 14 spue pressure whether be more than pre-level pressure, judge whether excavator is in standby mode.
When boost pressure increase want no detection unit 300 to be judged to be that excavator is in standby mode (there is not hydraulic pressure load) (step S21 is), controller 30 judges whether bar operation starts (step S22).In the present embodiment, controller 30, according to the output of pressure sensor 29, judges whether bar operation starts.
When being judged to be that bar operation starts (step S22 is), controller 30 stops the usual control (step S23) of nozzle aperture.Further, the boost pressure of controller 30 starting nozzle aperture increases control, the nozzle aperture of nozzle vane 25a is adjusted to nozzle aperture As (step S24) when increasing than boost pressure little when usually controlling.
And when being judged to be that bar operation does not start (step S22's is no), the controller 30 not boost pressure of starting nozzle aperture increases and controls, but the usual control (step S25) of starting nozzle aperture.This is in order to the nozzle aperture of nozzle vane 25a is adjusted to the nozzle aperture corresponding with engine speed.
In addition, when boost pressure increase want no detection unit 300 to be judged to be that excavator is not in standby mode (hydraulic pressure load) (step S21's is no), such as be judged to be main pump 14 spue pressure for more than pre-level pressure when, controller 30 also not starting nozzle aperture boost pressure increase control, or stop the boost pressure of nozzle aperture to increase control, the usual control (step S25) of starting nozzle aperture.
In addition, whether boost pressure increases wants no detection unit 300 can be also more than pre-level pressure according to the pressure that spues of main pump 14, or whether have passed through the scheduled time after stopping the usual control of nozzle aperture, or their combination, judge whether excavator is in standby mode.
Like this, controller 30, when bar operation starts, temporarily reduces the nozzle aperture of nozzle vane 25a.Therefore, even if controller 30 is when the hydraulic pressure load caused because of external force not yet occurs, the boost pressure of variable nozzle turbine 25 can also be increased.That is, before the hydraulic pressure load caused because of external force increases, boost pressure can be increased predetermined amplitude.Its result, even if variable nozzle turbine 25 is when the hydraulic pressure load caused because of external force sharply increases, also can decline (workability decline) causing engine speed or before engine stopping, producing the boost pressure corresponding to the hydraulic pressure load increased according to external force.In addition, when the increase of boost pressure does not catch up with the increase of the hydraulic pressure load (engine load) because external force causes, engine 11 fully cannot increase fuel injection amount, reduces engine speed, according to circumstances, cannot engine speed be increased and directly stop.
Then, illustrate that the boost pressure performing Fig. 8 increases the various physical quantitys passing in time when processing with reference to Fig. 9.In addition, Fig. 9 is the figure representing that these various physical quantitys are passed in time, from the upper operational ton of indication rod successively, hydraulic pressure load (absorbed horsepower), nozzle aperture, boost pressure, fuel injection amount and engine speed passage of time separately.In addition, passing indicated by the solid line in Fig. 9 represents that the boost pressure performing Fig. 8 increases passing when processing, and passing represented by dashed line in Fig. 9 represents that the boost pressure not performing Fig. 8 increases passing when processing.
In the present embodiment, suppose such as to have carried out situation about operating for the bar of mobile dipper 5 to carry out excavating at moment t1.
First, in order to compare, illustrate that the boost pressure not performing Fig. 8 increases the various physical quantitys passing in time when processing.In addition, the bar operational ton passing in time of dipper action bars is identical with the situation of Fig. 6, and therefore the description thereof will be omitted.
When the boost pressure not performing Fig. 8 increases process, hydraulic pressure load (with reference to dotted line) does not increase but passes unchangeably to moment t2.Afterwards, if at moment t2, dipper 5 touches ground, then with excavate counter-force increase correspondingly, hydraulic pressure load increase.
In addition, boost pressure (with reference to dotted line) is also do not increase to moment t2 but pass unchangeably, is also in lower state at moment t2.Therefore, variable nozzle turbine 25 cannot make the increase of boost pressure follow the increase of the hydraulic pressure load after moment t2.Its result, engine 11 fully cannot increase fuel injection amount, causes the deficiency that engine exports, and cannot maintain engine speed and reduce engine speed, sometimes cannot increase engine speed and directly stop.
And when the boost pressure performing Fig. 8 increases process, the nozzle aperture (with reference to solid line) of nozzle vane 25a starts to reduce at moment t1, before moment t2, be reduced to predeterminated level.Therefore, boost pressure (with reference to solid line) starts to increase at moment t1, before moment t2, increasing to predeterminated level.Therefore, variable nozzle turbine 25 after the time t 2, also can postpone not significantly in hydraulic pressure load increase increase boost pressure.Its result, engine 11 can not cause the deficiency that engine exports, and can maintain engine speed (with reference to solid line).
In addition, if at moment t2, the hydraulic pressure load of main pump 14 rises, then controller 30 is judged to be that excavator is not in standby mode, stops the boost pressure of nozzle aperture to increase and controls, start and usually control.Its result, nozzle aperture is controlled as the value corresponding with engine speed.In addition, in fig .9, for the ease of understanding, nozzle aperture when usually controlling is represented as passes with certain value, but in fact according to changes such as engine speeds.
Like this, controller 30, after bar operation starts, before the hydraulic pressure load increase that external force such as excavating counter-force causes, reduces the nozzle aperture of nozzle vane 25a, thus boost pressure is increased to higher level.Its result, even if controller 30 is when the hydraulic pressure load caused because excavating the external force such as counter-force suddenly increases, also can increase rapidly the boost pressure being in higher level.In addition, when increasing boost pressure, engine speed decline (workability decline), engine 11 also can not be caused to stop.
Above, describe the preferred embodiments of the present invention in detail, but the invention is not restricted to above-described embodiment, various distortion and displacement can be implemented to above-described embodiment without departing from the scope of the invention.
Such as, in the above-described embodiments, compressor blade 25d be subject to the emission gases of engine 11 and turn round the air entry making outer gas forcibly flow into engine 11 together with pivotal turbo blade 25b.But, the invention is not restricted to this structure.The revolution of compressor blade 25d such as shown in Figure 10, also can be controlled by supercharger electro-motor 60a.Specifically, supercharger electro-motor 60a changes rotating speed according to the control signal from boost pressure adjustment part 60.In this case, do not need turbo blade is turned round by the emission gases of the exhaust opening 11a of engine 11.
In addition, in the above-described embodiments, the discharge-amount of main pump 14 controls according to negative control and is controlled, but also can be controlled according to just control, Loadsensing control etc.
In addition, in the above-described embodiments, rotating mechanism 2 is fluid pressure type, but rotating mechanism 2 also can be electrodynamic type.
In addition, in the above-described embodiments, describe and be suitable for example of the present invention in the excavator by means of only engine 11 Host actuating pump 14, but the present invention can also be applicable to engine 11 and motor generator set to be connected to the excavator that main pump 14 carrys out Host actuating pump 14.In this case, the rotary motive power of engine 11 can be converted to electric energy by motor generator set by excavator, and in electrical storage device, accumulate this electric energy.Further, the electric energy accumulated in electrical storage device can be converted to rotary motive power by motor generator set and carry out Host actuating pump 14.
Claims (6)
1. an excavator, possesses:
Lower running body;
Upper rotation, is mounted on above-mentioned lower running body;
Swing arm, is arranged in above-mentioned upper rotation;
Swing arm cylinder, drives above-mentioned swing arm;
Dipper, is arranged on above-mentioned swing arm;
Dipper cylinder, drives above-mentioned dipper;
Hydraulic pump, is mounted in above-mentioned upper rotation, and to above-mentioned swing arm cylinder and above-mentioned dipper cylinder supply working oil;
Internal combustion engine, is mounted in above-mentioned upper rotation, possesses supercharger, and is controlled as certain rotating speed under the state be connected with above-mentioned hydraulic pump; And
Control device, controls the rotating speed of above-mentioned supercharger,
Above-mentioned control device increased the rotating speed of above-mentioned supercharger to increase the boost pressure of above-mentioned supercharger before applying hydraulic pressure load.
2. excavator according to claim 1, wherein,
Above-mentioned supercharger is variable nozzle turbine,
Above-mentioned control device, by reducing the nozzle aperture of the variable-nozzle in above-mentioned variable nozzle turbine, increases the rotating speed of the above-mentioned supercharger applied before hydraulic pressure load.
3. excavator according to claim 1 and 2, wherein,
The rotating speed of above-mentioned supercharger is controlled by supercharger motor.
4. excavator according to any one of claim 1 to 3, wherein,
There is switch, switch the work/stopping of the adjustment of the rotating speed of the above-mentioned supercharger applied before hydraulic pressure load.
5. excavator according to any one of claim 1 to 4, wherein,
Above-mentioned control device controls the rotating speed of the above-mentioned supercharger applied before hydraulic pressure load according to atmospheric pressure.
6. excavator according to any one of claim 1 to 5, wherein,
Above-mentioned control device starts the adjustment of the rotating speed carrying out the above-mentioned supercharger applied before hydraulic pressure load according to bar operation.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2013-184474 | 2013-09-05 | ||
| JP2013184474A JP6385657B2 (en) | 2013-09-05 | 2013-09-05 | Excavator |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104420496A true CN104420496A (en) | 2015-03-18 |
| CN104420496B CN104420496B (en) | 2017-04-12 |
Family
ID=52583508
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410400101.8A Active CN104420496B (en) | 2013-09-05 | 2014-08-14 | Shovel |
Country Status (3)
| Country | Link |
|---|---|
| US (1) | US9790664B2 (en) |
| JP (1) | JP6385657B2 (en) |
| CN (1) | CN104420496B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106013316A (en) * | 2015-03-26 | 2016-10-12 | 住友重机械工业株式会社 | Excavator |
| CN107923300A (en) * | 2015-12-25 | 2018-04-17 | 株式会社Kcm | Work machine |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6177913B2 (en) * | 2013-07-24 | 2017-08-09 | 住友建機株式会社 | Excavator and control method of excavator |
| JP6220228B2 (en) * | 2013-10-31 | 2017-10-25 | 川崎重工業株式会社 | Hydraulic drive system for construction machinery |
| EP3112539B1 (en) * | 2014-02-24 | 2017-11-22 | Sumitomo (S.H.I.) Construction Machinery Co., Ltd. | Shovel and shovel control method |
| JP6572160B2 (en) * | 2016-03-16 | 2019-09-04 | 日立建機株式会社 | Work vehicle |
| EP3425211B1 (en) * | 2016-09-28 | 2021-05-05 | Hitachi Construction Machinery Co., Ltd. | Work vehicle with confluence control device |
| JP7106949B2 (en) * | 2018-04-04 | 2022-07-27 | コベルコ建機株式会社 | Construction machinery engine system |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11181823A (en) * | 1997-12-19 | 1999-07-06 | Komatsu Ltd | Control method and device for construction machinery |
| US20120253610A1 (en) * | 2011-04-01 | 2012-10-04 | Anders Jonathan W | System and method for controlling power in machine having hydraulic and electric power sources |
| CN102979118A (en) * | 2011-09-06 | 2013-03-20 | 住友建机株式会社 | Construction machinery |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3191483B2 (en) * | 1993-03-31 | 2001-07-23 | いすゞ自動車株式会社 | Control device for turbocharger with rotating electric machine |
| US5468126A (en) * | 1993-12-23 | 1995-11-21 | Caterpillar Inc. | Hydraulic power control system |
| US6427445B1 (en) * | 2000-02-10 | 2002-08-06 | International Engine Intellectual Property Company, L.L.C. | Variable nozzle turbine control strategy |
| WO2002029230A1 (en) * | 2000-10-05 | 2002-04-11 | Nissan Motor Co., Ltd. | Control of turbocharger |
| JP3873742B2 (en) * | 2001-12-28 | 2007-01-24 | いすゞ自動車株式会社 | Control device for variable capacity turbocharger |
| JP2007071116A (en) * | 2005-09-07 | 2007-03-22 | Toyota Motor Corp | Turbocharger system with motor-driven assist function |
| GB2434421A (en) * | 2006-01-20 | 2007-07-25 | Bamford Excavators Ltd | A backhoe loader having ABS braking |
| JP4729446B2 (en) * | 2006-06-29 | 2011-07-20 | キャタピラー エス エー アール エル | Work machine output control device and work machine output control method |
| JP2008128107A (en) * | 2006-11-21 | 2008-06-05 | Hitachi Constr Mach Co Ltd | Output control device for working machine |
| JP2009191745A (en) * | 2008-02-14 | 2009-08-27 | Toyota Motor Corp | Control device for internal combustion engine |
| CH699804A1 (en) * | 2008-10-29 | 2010-04-30 | Alstom Technology Ltd | Gas turbine plant with exhaust gas recirculation and method for operating such a plant. |
| JP2010169242A (en) * | 2009-01-26 | 2010-08-05 | Sumitomo (Shi) Construction Machinery Co Ltd | Hydraulic drive mechanism for construction machine |
| EP2466018B1 (en) * | 2010-12-17 | 2019-11-13 | Caterpillar Inc. | Closed loop drive circuit with external brake assist |
-
2013
- 2013-09-05 JP JP2013184474A patent/JP6385657B2/en active Active
-
2014
- 2014-08-14 CN CN201410400101.8A patent/CN104420496B/en active Active
- 2014-08-28 US US14/471,219 patent/US9790664B2/en active Active
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11181823A (en) * | 1997-12-19 | 1999-07-06 | Komatsu Ltd | Control method and device for construction machinery |
| US20120253610A1 (en) * | 2011-04-01 | 2012-10-04 | Anders Jonathan W | System and method for controlling power in machine having hydraulic and electric power sources |
| CN102979118A (en) * | 2011-09-06 | 2013-03-20 | 住友建机株式会社 | Construction machinery |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106013316A (en) * | 2015-03-26 | 2016-10-12 | 住友重机械工业株式会社 | Excavator |
| CN107923300A (en) * | 2015-12-25 | 2018-04-17 | 株式会社Kcm | Work machine |
| US10662617B2 (en) | 2015-12-25 | 2020-05-26 | Hitachi Construction Machinery Co., Ltd. | Work machine |
| CN107923300B (en) * | 2015-12-25 | 2020-06-19 | 日立建机株式会社 | Working machine |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2015052277A (en) | 2015-03-19 |
| CN104420496B (en) | 2017-04-12 |
| US20150063967A1 (en) | 2015-03-05 |
| US9790664B2 (en) | 2017-10-17 |
| JP6385657B2 (en) | 2018-09-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104420496A (en) | Shovel | |
| US10577776B2 (en) | Shovel and method of controlling shovel | |
| JP6177913B2 (en) | Excavator and control method of excavator | |
| US20070033938A1 (en) | Engine system with a supercharger | |
| KR102440581B1 (en) | Engine system | |
| CN105026773A (en) | Engine-assist device and industrial machine | |
| US8538612B2 (en) | Device for controlling hybrid construction machine | |
| KR101778902B1 (en) | Work machine hydraulic energy recovery device | |
| US10302028B2 (en) | Work machine, power unit, and diesel engine of work machine | |
| JP2008128107A (en) | Output control device for working machine | |
| WO2011099326A1 (en) | Engine | |
| CN106211784B (en) | Variable pressure for variable delivery pump limits | |
| JP7148328B2 (en) | construction machinery | |
| JP5614814B2 (en) | Hydraulic work machine | |
| KR100521553B1 (en) | Intake booster | |
| KR102183217B1 (en) | Engine system using hydraulic system | |
| JPH11125187A (en) | Control device of variable displacement hydraulic pump | |
| KR101799731B1 (en) | Control system for engine provided with variable geometry turbocharger | |
| KR20030049688A (en) | the structure of variable shape of turbo charger and the controlling device and a method | |
| WO2022256178A1 (en) | System and method for controlling engine operations | |
| JP2015063847A (en) | Work vehicle |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |